Hydraulic gear shifting and driving system



Jan. 18, 1944. c. E. LINDEN ET AL 2,339,604

HYDRAULIC GEAR SHIFTING AND DRIVING SYSTEM Filed Oct. 14, 1940 6Sheets-Sheet 1 y vmz IV. xa-m W ATTORNEY! Jan. 18, 1944, 5 UNDEN ET AL2,339,604

HYDRAULIC GEAR SHIFTING AND DRIVING SYSTEM Filed Q0121 1.4,1940 6Sheets-Sheet 2 L'Il Jan. 18, 1944. c. E. LINDEN ETAL 2,339,604

HYDRAULIC GEAR SHIFTING AND DRIVING SYSTEM Filed Oct. 14, 1940 6Sheets-Sheet 3 1Z5 a MENTOR; @J CW0? 1 BY W 2! mad;

ATTORNEYJ C. E. LINDEN ETAL HYDRAULIC GEAR SHIFTING AND DRIVING SYSTEMJan. 18, 1944.

Filed Oct. 14, 1940 6 Sheets-Sheet 4 wxxm ' NVENTOR. BY @Mz 20 -664,

ATTORNEY:

Jan. 18, 1944.

HYDRAULIC GEAR SHIFTING AND DRIVING SYSTEM Filed Oct. 14, 1940 6Sheets-Sheet 5 c. E. LINDEN ET AL 2,339,604

Jan. 18, 1944. c. E. LINDEN ETAL HYDRAULIC GEAR SHIFTING AND DRIVINGSYSTEM Filed Oct. 14, 1940 e Sheets-Sheet e 2-4.M A TO NEY:

i this purpose.

Patented Jani18, 1944- UNITED. STATES PATENT OFFICE HYDRAULIC GEARSHIFTING AND DRIVING SYSTEM:

Carl E. Linden, Norwood, and Raymond B. McClellan, Hamilton, 'Ohio,assignors to The Fosdick Machine Tool Company, Cincinnati, Ohio, acorporation of Ohio Application October 14, 1940, Serial No. 361,044

' 15 Claims. (01. -129) This invention relates to gear shifting and isparticularly directed to hydraulic apparatus for More particularly, theinvention is directed to a fluid system, including valves and shiftingmeans for bringing about the shifting of the gears, and at the sametime, controlling the pressure, whereby it is suitable either forshifting gears or for driving the feed mechanism,

of a drill spindle or the, like. The hydraulic pressure employed forshifting the gears must be lower than that employed for driving aspindle feeding fluid motor in order to avoid undue shock in shiftingand to prevent breakage of the shifting mechanism.

Accordingly, it has been one of the objects of the present inventors toprovide s. pressurecontrolled and controlling apparatus in the hydrauliccircuit. This mechanism is automatic and is efiective for changing thepressure, preferably when a main clutch lever; that is, the clutch levercontrolling a drill spindle drive, is operated. When the lever is in anintermediate or neutral -range, which may be called the gear-shiftingrange, pressure is lowered. When the clutch is 'shifted to eitherforward or reverse, at which times the fluid is connected to the feeddrive for the spindle, the mechanism is efiective for raising thepressure. At these times, the fluid is cut ofi from the hydraulicgear-shifting portion of the mechanism and no damage can result. I

It has been a further object of the inventors to provide a system forhydraulic gear-shifting or driving, wherein the fluid is normallybypassed when the shifting or driving operations are r of valveelements.

closed position when released. In this arrangement, there is nopossibility of the shifting pressure passing through to thegear-shifting devices unless the clutch lever is in neutral and theshifting control valve is open. Thus, any possibility of improperoperation is eliminated.

It has been a further object of these inventors to provide an improvedgear shifting valve for controlling the application of hydraulicpressure. In this phase of the invention, a valve has been providedwhich can accomplish a. great number of shifts through a very compactarrangement One embodiment of the concept, and the preferred one,consists of a pair of valve elements operated through the same settingmeans, one of these elements being indexed in any one of a number ofpositions each time the other is rotated through a complete revolution.

. By locating these valves on the same axis and in not being performed,and wherein a relief valve permits this by-passing and automaticallycloses instantly when an operation is started, so as to 7 provide theproper pressure for the particularopthe operator may bring about theshift when he desires, assuming, of course, that the main clutch leveris in the neutral range; that is, the

, spindle driving means is unclutched.

Likewise, it is provided that this manually controlled shiiting valve isimmediately returned to the same casing, the valve arrangement is madevcompact and unified.

Other. phases of the invention relate to the structure of the valvecasing and movable elements, wherein an improved arrangement andrelationship of the ports and passageways is provided.

Other objects of the presentv invention relate generally to thearrangement of the various elements for bringing about the control ofthe degree of pressure for gear shifting and spindle number of operatingelements are required, and wherein the operation, wherein a apparatusoperates efiiciently without any chance of mishandling or failure tooperate in the prescribed manne Hydraulic feed driving means able inthat an infinite range of obtained. The rate of spindle feed may bedelicately adjusted through a needle valve or the like. However, it isnecessary that provision be made for tap lead feeds, and in this case,it is is highly desirdesirable that the feeds be mechanically drivenfrom the spindle so that the rate of feed is directly proportional tothe rate of spindle speed. When the spindle is being driven in any ofthe high speeds, it would be undesirable to engage any of the tap leads,because of the possibilities of tool breakage and the strain which wouldbe placed on the machine.

Accordingly, it has been another object of the 7 present inventors toprovide a hydraulic spindle feeding mechanism, which can be delicatelycontrolled by means of a throttle valve, same time, to provide means forconverting the drive from hydraulic to mechanical for the purspeeds maybe and at the I pose of the feeds for tap leads. Also, it has been theobject to provide a safety or lockout device for preventing shifting orcoupling of the driving means to the tap lead transmission when thespindle is being driven in the high speed range. According y. it will beimpossible to shift from the hydraulic feeding means to the tap leadfeeds when the hydraulic feeding means is operating at high speed.

Other objects and certain advantages of the invention will be more fullyapparent-from the description of the drawings in which;

Figure 1 is a general perspective view, illustrating a radial drillincorporating the improved gear-shifting and control mechanism of thisinvention. a Figure 2 is a fragmentary sectional view taken on line 22vthrough the head, illustrating the mounting and relationship of theselector valve, its operating means, and the indicator device.

Figure 3 is a sectional view taken on line 33, Figure 2, illustrating indetail the indexing and operatingmeans of Geneva gear form for movingone of the valve elements to one of eight different positions upon eachrotation of the other valve element.

Figure 4 is a fragmentary face view of the indicator.

Figure 5 is a top plan view of the valve body.

Figure 6 is a side view thereof.

Figure 7 is an end view thereof. a

Figure 8 is a developed view, showing the porting and groovingarrangement of the two valve elements.

Figure 9 is a longitudinal sectional view of the valve elements.

Figure 10 is an end view of'the main valve element.

Figure 11 is a general sectional view, showing the tap. lead feedtransmission relative to the spindle.

Figure 12 is a sectional view taken on line i2-l2, Figure 1,illustrating the hydraulic motor feed drive and its control means.

Figure 13 is a sectional view, taken on line I 3-l3, Figure .12, showingthe shifting means for controlling the hydraulic and mechanical feeds.

Fi ure 14 is a detailed sectional view taken through the lock-out valvefor preventing shifting fromhydraulic feed to mechanical feed when thespindle is in the high speed range.

Figure 15 is a sectional view taken on line IS-IS, Figure 12.

Figure 16 is a diagrammatic view showing the hydraulic circuit and thevarious valve elements and operating means.

manually operated valve is held open. A pressure regulating valve isinterposed in the fluid line, leading to the selector valve and iseifective for accomplishing low gear-shifting pressure and relativelyhigh hydraulic motor driving pressure for a spindle or the like. I

Referring to the drawings, the sump or fluid reservoir idiagrammatically shown in Figure 16 at IS. The pump l6 has itsintakepipe H extended to the sump l5. Its delivery pipe l8 delivers the fluidinto a relief valve I! of the vented type. This valve I 9 incorporates-acasing 20 and a valve element 2| operating in a chamber 22 and urgedinto closed position by means of a spring 23. The casing includes whichthe valve rests when the passed. The valve element 2| includes a taperedseating extension 25 adapted to engage over a by-pass outlet 26 fromwhich a pipe 21 leads to the sump I5, The main delivery pipe 28 extendsfrom the chamber 22 diametrically opposite the pipe I8. This pipe 28extends to the main control valve 29, operated by the clutch lever 30.Normally, some of the fluid from the pump I6 is defluid i beingbylivered through pipe I 8 into the chamber 22 and.

out through the exhaust or by-pass 2'|.

The spindle, generally indicated at I22 later on in the description, isdriven in the usual conventional manner by means of power on the arm,

to close. Closing Generally described, the present apparatus I providesa source of hydraulic pressure, such as a pump which may be driven bythe spindle transmission. This pump delivers the fluid through a ventedtype relief valve which either by-passes the supply or directs it intothe system for shifting the gears and for driving the feed drive motor.The delivery of the fluid is controlled manually through the clutchlever which either directs it to the feed drive at the time the clutchis conthe fluid topass such as an electric motor shown in Figure 1. Itis not believed necessary to describe this transmission of power indetail. The clutch lever 30 shown in Figure 1, in addition to shiftingthe conventional clutch, also operates the valve element 43 of the valve29 shown in Figure 16. The clutch referred to controlsthe connection ofthe power to the spindle.

Now, in order for the delivery of fluid to take place through line 28for building up a shifting or driving pressure, it is necessary for thevalve 2| of this valve occurs when there is fluid pressure balance aboveand below the valve 2|, and the spring 23 is effective. For thispurpose,- the valve 2| is vented as at 3|, permitting through it to thechamber 32 above the valve. The chamber 32, containing the spring abovethe valve, is connected to either one of two valves 33 and 31, whichunload respectively in a high pressure range such as 500- 600 pounds persquare inch and a low pressure range of -175 pounds pressure per squareinch. An automatic pressure control valve 34 controls the connection ofthe chamber 32 to the respective unloading valves.

When the line 28 is blocked; that is to say, the oil accumulates underpressure beneath the valve 2|, the valve element 2| remains off theseat, the oil by-pa'ssing through the pipe 21. Relief of the chamber 32takes place at the pressures at which valves 33 and 31 are set tounload, and this permits the pumping pressure to hold the valve valve33, and a pipe 36 extends from the pipe 35 to the unloader valve 31through the automatic control valve 34.

The delivery pipe 28 extends to the valve 29, and the pipe 38 extendsfrom the valve 23 through a manually operated gear shift control valve39, which in turn is connected to the selector valve by way of a pipe40. From the selector valve 4 i, the oil i distributed as directed bythe control passageways to the shifting devices, one of which isindicated, at 42. The main clutch lever 30, operating the clutch whichcontrols the power a shoulder 24 against ment between two positions.

- respective springs is set a set screw 59 including a thrust head,movable the respective pipes to the sump l5 through pipes 60-450. Thevalve connection to the spindle is connected to the valve element 43 ofthe valve 29 by means of a link 44. The line 28 branches as at 45 fordellvering the fluid into the bore of the valve 29 over an intermediateportion of its length. The pipe 38 extends from the bore, intermediatethe inlets of the branch passageways 45. The valve element 43 includesan annular circumferential-groove 48 of some length intermediatethereof. Thus, through an intermediate the clutch lever, representingthe neutral position of the clutch, the valve may be moved withoutdisturbing the flow through to the control valve 39 and the selectorvalve 4i.

At either side of the pipe 38. where it enters the valve 29,'the branchpassageways 4I-41 connect to a main pipe 48, extending to the feed drivemotor 49, from which the oil is delivered back to the sump I5. A feedrate control or throttle valve 50 is interposed in the line 48. Thevalve eleof the valve 50 may be rotated in screw threads 52 foradjusting the rate of flow of the oil to the motor 49. Thus, when themain clutch lever i moved to either forward or reverse drive positions,the oil is connected for delivery to the feed drive motor, for atportion of the swing of that time, the annular chamber above the valve2| of the relief valve is only connected to the unloader valve 83, andthe unloading must take place through this valve. Accordingly, the oilis delivered to the feed drive motor at the higher pressure.

The shifting control valve 39 consists of a casing 65, in which a valveelement 66 is slidably mounted. The valve element, externally of thecasing, includes an annular groove engaged by the pin of an arm 88. Thearm is swung by means of the hand lever 69 journalled in the side wallof the head stock casing 10. The valve element includes upper and lowerexternal shoulders, the lower shoulder consisting of a slidably mountedwasher element 1| normally held in its abutting position by means of acoil spring 12. This spring is held under pressure, against the washerII, about the lower extended end of the valve element by a washer l3,fixed on the valve for moving groove 46 connects branch passageways withone of the branch passageways. Obviously, the flow to the gear-shiftingmechanism is cut off at either of these positions.

As stated heretofore, it is requisite that the pressure be low for gearshifting and high for motor driving. In order to bring this about, the

automatically-operated, pressure-controlled valve 34 is connected to thegear shift delivery line 38 by means of a pipe 53, This valve element 54which is shuttled back and forth When the oil is flowing through to thegear shifting side of the apparatus and live oil is in the pipe 38, thevalve element 54 will take the position shown in the drawings (Figure16). At this time, the oil above the valve element 2| of the reliefvalve I9 may pass through the line 36 into an annular groove in theshuttle valve element 54 and to the low pressure unloader valve 31.

The valves 33 and 31 are duplicates except for valve 34 includes a theweight andtension of their respective springs 5'I-51. They consist ineach case of a needle type v'alve element 58, normally urged downwardlyby means of the spring 51 to block the flow of fluid through a here. Thetension of the in each case by means of valve element. In each case, 35and 36 exhaust the oil toward and from the 31, as stated, is set tounload at low pressures, such as 125-175 pounds per square inch.

- Now, as the valve element43 of the main con-' trol valve is shifted tofeed drive positions, the

oil supply to the automatic pressure-controlled valve 34 is cut off andthe spring 8| of the automatic valve will move the shuttle valve element54 downward so as to block the flow of oil to the unloader valve 31. Atthis time, the only point at which the loaded is at the valve 33, whichis set to unload in the high pressure feed driving range. The oil maybleed back into the sump I5 from the lower portion of the bore of theautomatic valve to permit return of the valve. This bleeding, however,is not sufficient to interfere with the normal operation of the system.

When the high pressure condition exists, the

element. Thus, the valve element may be lifted the annular groove 14thereof into position, connecting the pipes 38 and 40, but will bereturned to shut-off position when thehandle is released by means of thespring 12. When the valveis open, the oil flows into the selector valve.

The selector valve comprises, generally, a casing 15 and a pair ofrotatable valve elements TIE-11 in the casing, disposed in end-to-endabutment; that is, on the same axis. A selector cranklever I8 is pinnedto the'lower end of a rod I9. The upper end of the rod carries a bevelgear 80, meshing with a bevel gear 8| on the axis of the valve elements.A second bevel gear 82 is pinned to the shaft I8 and meshes with a bevelrin gear 83, fixed to a shaft 84, carrying the indicator 85. The gears82 and 83 are disposed in a casing 86 (Figure 2) mounted about andtraversed by the shafts I9 and '84. A circular frame element 81 isattached to the front face of the head stock casing 10, and theindicator dial rotates within and adjacent the opening 88 in the element81. The graduations, indicating speeds from 15 R. P. M. to 1,000 R. P.M. are arranged'around the tapered marginal face of the dial and moverelative to an indicator finger 89,

to the shaft 90. This gear meshes with another gear 93, fixed to one endof a shaft-94, journalled in upwardly extending arms 95 respectively ateach end of the valve body 15. The other ,end

of theshaft 94 carries the driving arm 98 of a pressure may be relievedorun-' Geneva gear mechanism. The roller 91 on the end of the arm isadapted to successively engage (Figure 3) the notches 98 of the Genevagear element 99. This Geneva gear element is formed at the outer end ofa sleeve element I00, extended into the bore of the valve element 11 andin splined .connectiontherewith. The ends of the valve body are closedby means of heads IOI, which heads form the bearings for the gear 82 andthe Geneva gear element 99. A collar I02 is'pinn'ed to the end of theshaft and holds the element 99 in position.

Both the gear 92 and the Geneva gear element 89 carry indexing or detentplates I03. These 11 is rotatedthrough a pin I08 in the outer end ll isinserted in the intermediate portion'of warm I 05. pivoted on a pin I06in a lug of the head IOI. The outer end of the arm I is pulleddownwardly by means of a coil spring III'I under tension between of thearm and a pin I09 in the lug III of the head IOI. This detentarrangement is provided for each detent plate I03; that is, themechanism Just described is duplicated at each end of the valve. Thus,the valve element 11 is intermittently moved and indexed for accuratepositioning. Each time the main valve element 15 makes a completerevolution, the valve element 11 makes a one-eighth turn. Thus, thepositions ofthe main valve are repeated with shifting variationsachieved at the indexed positions of the second valve element.

' The delivery line 40 enters a longitudinal bore III inthe valvecasing. From this bore, the oil is distributed radially, inwardlythrough the six radial ports II2. These ports communicate withcircumferential grooves 3, equally spaced along the peripheries of the"respective valve elements IS-I1. The circumferential grooves Ill,disposed between the groove f I3, may be referred to as exhaust grooves.Each of these-grooves is in constant communication with the sump, as

showndiagrammatically in Figure 16 (see the pipes II 5). The groovesII3I I4 include longitudinal dead-ended extensions II6, the ends ofthese grooves cooperating or registering with the ports III (Figure 6).ment, the ends of the gear-shifting cylinders may be alternatelyexhausted and charged. The valve casing element includes feet I25 forattaching it in position in the upper end of the head stock casing.

A typical arrangement is shown in Figure 16.

' The illustration in this figure is diagrammatic of the structure shownin Figure 11, the details of the spindle and spindle sleeve beingomitted. A gear-shifting device 42 consists of a cylinder H8 and apiston of the plunger carries a yoke I20 engaged with the conventionalgroove of a coupling element I2 I. In one position, the coupling elementeither couples the spindle shaft I22, upon which it is splined with thegear I23, or in another position, couples the shaft with the gear I24.

In the position shown, the shifting plunger has its upper end connectedto the exhaust roove Ill by means of a pipe I25, extended into one ofthe ports I IT. The lower end of the cylinder is charged through a pipeI26 extending into one of the ports I" in communication with a charginggroove H3. Itwill be obvious that the longitudinal, dead-ended slots,determine between them by their arrangement and by the coupling Throughthis arrangeor plunger H9. The outer end of the pipes the order andsequence of the shift-.

A gauge I30 is interposed in the delivery line 28 for indicating thepressure at which the oil is delivered into the system. Also a gearspray line 28 and is efiective for lubricating the transmission.

Description of operation Speed changes are accomplished in the followingmanner: Regardless of whether or not the clutch lever 30 is in forwardor reverse or neutral, the desired speed may be selected by rotating thecrank 18 to bring the dial to the correct point relative to theindicator. The valve elements I6 and 11 have then been set for chargingand discharging the proper shifting devices of the system. Assuming thatthe clutch lever is in or the feed drive motor is being operated. .The

oil from the pump is' delivered into the valve I9. It enters the chamber22 and will by-pass through the pipe 21 unless the element 2I moves downto cut oil the flow through the pipe 21. The fluid also passes throughthevent 3| to the chamber above the element 2I. This chamber is blockedat all times by the unloader valves. The unloader valve 31 is set tounload at approximately pounds per square inch, which is a/pressuresuitable for gear shifting, and the unloader valve 33 is set to unloadat approximately 500 pounds pressure per square men, which is thecorrect pressure for operating the feed driving motor. The delivery pipe28 is also normally blocked either at the valve 29 or at the valve 39,or both.

Since the unloader valve 31 unloads at approximately 150 pounds, and thepump will develop a greater pressure, and due to the fact that thespring pressure on the valve has been carefully adjusted, the valve I9will not seat when the will seat during the operation of the feed drivemotor.

Having pre-set the selector valve to theldesired speed when the clutchhas been disconnected and the clutch lever is at neutral, operation ofthe shifting lever 69 will permit the oil to flow through pipes 28, 45,groove 46 of valve 29, pipe 38, through the groove of the valve element66, through pipe 40 into the pressure r o of the selector valve andthence through the selected conduits to the proper gear-shiftingdevices. At this time, pressure in the line 38 will move the automaticvalve element 54 to the position shown, and the shifting pressure cannotdevelop beyond 150 pounds per square inch, at which pressure it unloadsthrough the unloader valve 37 by way of pipe 36 and groov 55.

When the clutch lever is moved to either forward or reverse, thepressure in the line 38 is cut off and the automatic valve element 54drops down as the oil bleeds back into the sump. Pressure up to 500pounds will be developed, sufiicient for driving the feed drive motorthrough pipe 28, pipe 45, pipe 41; pipe 48, the throttle valve 50, tothe motor and thence into. the sump.

Tap lead drive lock-out means The hydraulic feed drive motor 49, beingcontrolled by the throttle valve 50, provides spindle feed ratessumciently accurate for straight drilling purposes. The utilization of ahydraulic motor for the tool feed is especially desirable because of theinfinite number of feed rates provided. The feeds for the tap leads mustnecessarily be positive. For this purpose, a tap lead transmission,indicated generally at M0, is provided. The transmission is driven fromthe spindle sleeve and so -its rate of speed is always di- -shaft of thehydraulic motor 49.

.rectly proportional to the rate of spindle speed.

' would be undesirable to engage any of the tap leads because of thepossibilities of tool breakage and the strain which would naturally beplaced on the driving parts of the machine.

To insure that an operator will not engage the positive tap feed whilethe spindle is in the high speed ranges, a hydraulically controlled taplead lock-out is provided for automatically holding the feed clutchelement out of engagement while the high speed ranges are being used.The lock-out comprises a piston I43 slidably mounted in a, cylinder I44and extending through the top and bottom of the casing of the cylinder.The lower extension I45 of the piston or plunger carries an arm I46pinned thereto. The upper extension of the plunger issplined at I41 sothat the plunger cannot revolve as it slides.

An oil line I48 coming into the cylinder I44 below the piston I43 isbranched from the line I26 which, when carrying pressure, effects the 1-major speed change in the train of gears driving the spindle. Thus,whenever oil pressure is directed to the gear-shifting device 42 forcoupling the smaller gear I23 of the two driven gears on the spindlewith the speed drive, the plunger I43, carrying the look-out arm, ismoved upwardly in its cylinder. The oil line I48 is-the only opening 'inthe cylinder I44, therefore, the plunger cannot move down unless theline I26 is exhausted.

The tap lead transmission is driven from agear I50 on the spindle sleeveII. A gear I52,

in mesh with the gear I50 on the sleeve, is

keyed to a stub shaft I53, journalled inball bearings in the top wall ofthe transmission casing. A pinion gear I54 on the other end of the stubshaft is in mesh with the upper one of a cluster of three gears I55,I56, and I51 respectively, on the inside of the transmission casing. Thethree gears are fixed on a splined shaft I58 which is journalled in ballbearings in the casing. On a second splined shaft I59, simtherefore notshown in more detail. The shaft I66- continues down and extends to theoutside of the machine. A hand wheel I14 is provided on the shaft I66 atthe outside of the machine for. manual operation of the feed' mechanism.

The feed clutch element I II has three posii tions; When up, a crowngear I on the top lace meshes with the crown gear I61 and the feed isfrom the hydraulic motor.

When down, the clutch element engages the gear I63 and the feed is fromthe transmission. In the intermediate position, both hydraulic andpositive feeds are disengaged, and the feed can be operated manually bythe hand wheel. The shiftilarly journalled, is a shiftable gear clustercomprising threegears I60, I6I, and I62, adapted to mesh with the gearsI55, I56, and I51. The six gears shown are proportioned to provide thethree standard tap lead changes; namely, 8,

11 and 14 threads pe'rinch. Below the slidable gear cluster a stationarygear I63 is journalled on the splined shaft I59.v This. lastmentionedgear is adapted to mesh with a gear I64 on the lower end of the feedclutch element I4I.

The feed clutch element is mounted on a splined portion I65 of. a shaftI66 and is slidable between the gear I63 of 'the feed :transmission anda crown gear I61 on the lower face of a helical gear or worm wheel I68.The helical .gear is journalled in ball bearings on the upper end of theshaft I66 and is in mesh with a worm gear I69 pinned to the forward endofthe drive The shaft I66 extends down vertically and carries a worm I10(shown in dot-dash lines only) for engagement with a gear I1I. Ashaft,I12 extending back from the gear "I carries. a pinion" I18 which is inmesh with a feed rack on the spindleable gear cluster, comprising gearsI60, I6I, and

I62, also has three positions. .Both the gear 1 cluster and the clutchelement are operated by a single hand'lever I16. The lever has twomovements, a horizontal swinging movement for shifting thegear clusterand a vertical pivotal movement, for operating the clutch I4I. Theslidablecluster of gears is shifted by a yoke I11, the arm I11a of whichis keyed to a shalt I18 journalled in the front wall of'the reedtransmission casing. The shaft I19 extends through to the lront of thecasing and carries a bevel gear I18. The arm of the yoke, extending atright angles to the shaft nil, imparts an arcua'te movement to the yoke.10 compensate for this, the yoke 111 is free to swing on a pin at rightangles to'the arm in the end thereof. The bevel gear I800, is pinned totheend of a horizontal shaft I which is journalleci in a bearing |8I atthe front of the casing. A similar bevel gear I82 at the other end ofthe shaft I80 is in mesh with a bevel gear I83 (Figure 12) keyed toavertical shaft I84.

The shaft I84 is moved by the hand lever I16.. As stated before, thehand lever has 'two swinging movements. The horizontal movement revolvesthe bevel gear I83 to shift the gear cluster through the connection justdescribed. The hand lever has three positions in its horizontal movementto correspond to the three positions of the gear cluster. Therefore,conventional detent means'mot shown) are provided to index the clusterin any one of these positions.- The clutch element I4I (Figure 16) isshifted by an arm I85 carrying a yoke I86 riding in a groove I81 in theclutch element. The yoke I86 is journalled in the arm in the samemanner" pivotally connected to the link I9I at its one end and has itsother end pivoted in a slot I93 in a collar I84. The collar I84 is notinfluenced by the rotative action ofthe vertical shaft I84 since it ison the shaft between two pinnedcollars I86-I96, and has its sideflattened, as at I91,

for sliding engagement with the front wall of the transmission casing.The link I9I is extended beyond its connection to the link I92 and isprosleeve; This arrangement of parts for the feed drive is a'ccording'tocustomary practice and is vided with a bushing I98 housing a springurged ball constituting detent means for holding the I yoke in itsvarious positions. Three recesses,

appropriately the ball.

Thebevel gear I83 is keyed to the vertical shaft I84 in a long keywayI99. The bevel gear is therefore only influenced by the rotativemovement of the vertical shaft. The vertical shaft is journaled at itsupper end in a block 200 at the front of the transmission casing. Thebevel gear I83 is provided with a long bearing sleeve 20I and isjournaled inside of the block 200 and held therein by a set screw 202threaded through a collar 203 on top of the-block. The vertical shaftpasses through the sleeve 20I, theblock 200, and the collar 203 andextends above them. A coil spring 204 disposed around the vertical shaftbetween a washer 205 resting on the collar 203 placed for the threepositions, seat on top of the block and a collar 206 pinned to the veryupper endof the shaft, provides a counterbalance for the shaft. This isprovided so that the shaft is easily shiftable vertically. Y

The lower end of the vertical shaft" is journailed in a bearing20lbolted to an inner wall of the headstock. ,A sleeve .208 keyed to thevertical shaft within the bearing 20|.provides a bushing for thebearing. The key is slidable in a long keyway 209 so 'that the verticalshaft is free to slide up and down therethrough. The lower end of thesleeve is enlarged and provided pressure of the fluid delivered by saidpump and adapted to bypass the fluid when delivery is blocked, a mainclutch lever for coupling power to said transmission, a valve operatedby said lever and adapted to be held in open position when the clutch isin neutral, a shifting valve,

a selector valve receiving fluid under pressure through said clutchlever operated valve and said shifting valve when said valves are open,and-shifting devices operated by said shifting valve as selected by saidselector valve.

2. A hydraulic system for shifting gears and feeding a, spindle,comprising a source of fluid pressure, means for regulating thepressure,a spindle feed driving motor, a selector valve for distributing thefluid for the shifting operations, a clutch lever controlled valve fordirecting the fluid either to the selector valve or to the spindle feeddriving motor, and a manually controlled shifting valve interposedbetween the clutch lever controlled valve and the selectorvalve,'whereby with 'arms'ZIll-flll for pivotally journallingtheshifting lever I16 therebetween on a cross pin 2| I. The enlargedportion of the sleeve 208 provides a shoulder 2 I 2 which rests againstthe lower face of the bearing zlll and cooperates with a collar .2I3around the upper end of the sleeve 208,

thus holding the sleeve in place in the bearing 201. This arrangementpermits the sleeve to rotate in the bearing but retainsit againstvertical movement.

.The indicia 2 I! for the various positions of the shifting arm are on astationary sleeve 2- mounted on and around the bearingdlll. An

' inverted cup-shaped element 2l5, having a, pointer 246 depending fromthe front edge-thereof; is pinned -to' the vertical shaft above thebearing. both rotatively and- The pointer' therefore moves reciprocablywith the vertical shaft.

Operation of the lock-out means When the spindle is in the lower speedranges;

that is, when the gear I24, the larger ofthe two on the spindle, isbeing driven, the side of the the fluid can be directed by said clutchlever controlled valve for permitting shifting of gearswhen the clutchis in neutral and feed driving when the clutch is in forward or reversepositions.

3. A hydraulic speed changing and spindle operating system, comprising afluid pump, a control valve, a shifting valve, a selector valve, gearshifting devices, a conduit system for supplying fluid to and throughthe respective elements in the order named, a relief valve interposed inthe system between the pump and the control valve, a clutch controllever for the spindle, said clutch control lever connected to saidcontrol valve, a spindle feeding hydraulic motor having fluid connectionto said control valve, said control valve in the neutral position ofsaid clutch lever adapted to deliver the fluid to the gear shiftingdevicesby way of the shifting valve and selector valve and in its drivecoupling positions adapted "rectly connected to the relief valve and theother connected to .the relief valve through the-automatic valve, saidrelief valve including a valve element normally unseated by fluidpressure when cylinder for the shifting device 42 which controls theengagement of gear I23 (the high speed range gear) is exhausted.Therefore, the oil line I to the lock-out is also exhausted, since itbranches from the line- I26. With the oil line I exhausted, the plungeris extended. through this arm and is adapted to rest on the top of thearm I46 plunger I" when the plunger is up and the clutch element isinneutral.

Therefore, the lock-out device, when under oil pressure from the line'l,

locks the clutch element "I from engagement with} the mechanical feedtransmission. 'The v lock-out occurs when the jclutch; element is in 1neutral, thus the hand feed can be utilized. Also, the lock-out armbeing below the extended pin on.

a transmission. comprising a fluid pump, a relief valve, an unloadervalve adaptedlto control the carried 'by' the for shifting the gears ofI43 carrying the lock-out arm dis free to bemoved..down. The pin on ithe yoke I86, mounted in the shifting arm I",

the system to the selectorvalve .and' hydraulic motor is closed andincluding a. port therethrough permitting the flow .of fluid above thesame to the unloader valves for causing the relief valve to close offthe bypass when the-fluid is being used either for shifting or driving.

4. A mechanism for controlling the driving of tap lead feeds, comprisinga spindle, a shifting device for connecting either high or low speeddrive to said spindle a transmission driven from said spindle for taplead. fee a hydraulic motor for alternatively driving-said tap 'lead'feeds, said transmission including a feed clutch element foralternatively coupling the transmission to ,said

tap feeding means or motor thereto, means for locking said feed clutchelement for movement either in intermediate neutral position or inhydraulic driving position,

4 taplead gear transmission when the high speed drive is'couple'dto saidspindle, a plunger supplied with'fluid from the shifting devicecontrolling the coupling of the low and high speed ranges to thespindle, said locking means when the high speed range is co'upl v 5. Ahydraulic systemfor controlling and operatinga' drill spindle,comprising a fluid pump,

for coupling the hydraulic ein charged valve.

said spindle and having operative connection for a control valve, ashifting valve, a. selector valve, gear shifting devices, a conduitsystem for supplying fluid to and through the respective elements in theorder named, a relief valve for controlling the fluid pressure, saidrelief valve interposed in the system between the pump and the controlvalve, a clutch control lever for the spindle, said clutch control leverconnected to said control valve, a spindle operating hydraulic motorhaving fluid connection to said control valve, said control valve in theneutral position of said clutch valve, a shifting valve, a selectorvalve, gear shifting devices, a conduit system for supplying fluid leveradapted to deliver the fluid to the gear shifting devices by way of theshifting valve and to and through the respective elements in the ordernamed, and a clutch control lever for the spindle, said clutch controllever connected to said control valve, said control valve in .theneutral position of said clutch lever adapted to permit delivery of thefluid to the gear shifting devices by Way of the shifting valveandselector '7. A hydraulic gear-shifting apparatus, comprising, a fluidpump for delivering fluid under pressure, a selector valve, means forpre-setting said selectorvalve, gear-shifting devicesserved by saidselector valve, conduit means connectin said pump to said selectorvalve, a clutch lever for controlling the power for the gears, manuallyoperated valve means in the conduit, and means between the pump and theselector valve for preventing delivery of fluid to the selector valveunless the clutch lever for controlling thepower is in neutral.

8 A hydraulic system for shifting gears and feeding a spindle drivingthe gears, comprising,

a spindle, gears driven by the spindle, gear-shifting *deviceS, a clutchlever for controlling the power to the gears, a hydraulically operatedspindle feed'motor, fluid delivery means, a selector valve controllingthe delivery of fluid to the respective shifting devices, and a valveoperated by said clutch lever for causing delivery of fluid to theselector valve, when the clutch lever is in neutral and delivery offluid to the feed motor when the clutch lever is in position forcoupling the power. i

9.'Av hydraulic system for changing gears, comprising a fluid pump, arelief valve, a delivery conduit passing through the relief valve, an

exhaust conduit from the relief valve, said relief valve including ashiftable element having a vent therethrough to permit the applicationof fluid pressure to both sides of the element, an unloader valve inconnection with the relief valve on the side of the shiftable elementopposite to the delivery and exhaust side, a speed selecting .feedingsaid spindle, said feed clutch element adapted to either connect saidhydraulic motor to said spindle or said tap lead transmission to saidspindle, feed clutch shifting means, driving gears 'in said spindlerotating means for said spindle for driving the same in low' and highspeed ranges, a hydraulic shifting device for said driving gears, ahydraulically operated plunger device connected to that side of thehydraulic shifting device which is charged when .the spindle drivinggears are in the high speed range, locking arms on the plunger and feedclutch shifting means adapted to be engaged for preventingmovement ofthe feed clutch element to tap lead transmission connection when thehigh speed spindle driving range is being used.

11. Mechanism for operating a dril1 spindle for tap lead feeds,comprising means for rotating the spindle, a tap lead transmissiondriven from said spindle and having operative connection for feeding thespindle, a feed clutch element and, a hydraulic motor in saidtransmission for directly feeding said spindle, s'aid feed clutchelement adapted toalternatively connect said hydraulic motor to saidspindle and said tap lead transmission to said spindle.

12. Mechanism for operating a drill spindle for tap leadfeeds,comprising driving gears for rotating the spindle, a tap leadtransmission driven from said spindle and having operative connectionfor feeding a spindle, a feed clutch element,

high speed ranges, a shifting device, for said driving gears, andlocking means adapted to be moved by said shifting device for-preventingmovement of the feed clutch element to transmission connection when thehigh speed spindle range is being used.

13. Apparatus for driving a spindle for tap lead feeds, comprising ahydraulic motor, a transmission extending from a rotative connection tothe spindle to a translative connection to the spindle, a shaft in saidtransmission carrying a hand wheel, a feed clutch element having -asplined slidable connection on said shaft, a

valve, shifting devices controlled thereby, valve means interposedbetween the relief valve and the selector valve and permittingdeliveryof fluid to the selector valve, said unloader valve limiting thepressure at-which the fluid is delivered and permitting the shiftablevalve element in the relief valve to remain in by -pass position whenthe. control valve is closed "and the supply is blocked to the selectorvalve.

10. Mechanism for tap lead feeds, comprising means for rotating thespindle, a tap lead transmission driven from for operating a drillspindle hydraulically driven means loosely mounted on the shaft andadapted to be coupled thereto by means of the feed clutch element, saidfeed transmission adapted to be coupled to the shaft' through said feedclutch element, and means for preventing movement of the feed clutchelement into transmission connection when the spindle is being driven inhigh speeds.

14. A mechanism for operating a drill spindle for forming tap leads,comprising a spindle,

means for rotating said spindle in high and low speed ranges, hydraulicmeans for shifting from one rangeto the other, a tap lead transmissiondriven from the spindle including a translative connection thereto,hydraulic means for feeding said spindle, a feed clutch elementioralternatively connecting said hydraulic means and said transmission tosaid spindle, and a lockoutdevice for locking the feed clutch elementout of the transmission drive position when the rotating means iscoupled to the spindle in the high speed range.

.low speed ranges and including a range changing device, a hydraulicmotor, a mechanical l5 drive through a transmission driven from thespindle,-hand operated shifting means for engaging either one of thefeed drives to the spindle, and a safety lock-out device for locking theshifting means from engaging the mechanical transmission when thespindle is being driven in its high speed range, comprising ahydrauliout position.

cally operated plunger charged from the speed range changing device forthe spindle driving transmission when the high speed range is connectedfor holding the look-out device in lock:

CARL E. LINDEN. RAYMOND H. MCCLELLAN.

